CN101344155B - 10-speed transmission - Google Patents

10-speed transmission Download PDF

Info

Publication number
CN101344155B
CN101344155B CN2008101376914A CN200810137691A CN101344155B CN 101344155 B CN101344155 B CN 101344155B CN 2008101376914 A CN2008101376914 A CN 2008101376914A CN 200810137691 A CN200810137691 A CN 200810137691A CN 101344155 B CN101344155 B CN 101344155B
Authority
CN
China
Prior art keywords
planetary gear
parts
gear set
torque transmitter
optionally
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN2008101376914A
Other languages
Chinese (zh)
Other versions
CN101344155A (en
Inventor
A·W·菲利普斯
S·H·维特科普
J·M·哈特
C·E·凯里
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GM Global Technology Operations LLC
Original Assignee
GM Global Technology Operations LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GM Global Technology Operations LLC filed Critical GM Global Technology Operations LLC
Publication of CN101344155A publication Critical patent/CN101344155A/en
Application granted granted Critical
Publication of CN101344155B publication Critical patent/CN101344155B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Abstract

The present invention relates to a ten grades transmission which has a plurality of members that can be utilized in powertrains to provide ten forward speed ratios and one reverse speed ratio. The transmission includes three planetary gear sets, six torque-transmitting devices, and two fixed interconnections. The powertrain includes an engine and torque converter that is continuously connected to one of the planetary gear members and an output member that is continuously connected with another one of the planetary gear members. The six torque-transmitting devices provide interconnections between various gear members, and the transmission housing, and are operated in combinations of three to establish ten forward speed ratios and one reverse speed ratio.

Description

10-speed transmission
Technical field
The present invention relates to a kind of power transmission with three planetary gear set, these planetary gear set are controlled by six torque transmitters, so that ten forward velocity ratios and a reverse speed ratio to be provided.
Background technique
Passenger vehicle comprises the dynamical system of being made up of motor, multiple-speed gear-box and differential retarder or main reducing gear (finaldrive).Multiple-speed gear-box repeatedly moves the whole service scope that has improved vehicle by allowing motor in its torque range.The number of times that the quantity of available forward velocity ratio decision Engine torque scope repeats in the speed changer.Early stage automatic transmission has two velocity ranges.This has seriously limited the whole velocity range of vehicle, and therefore needs to produce the relatively large motor of wide speed and torque range.This causes motor to operate in during cruising on the specific fuel consumption point that certain is not Available Point.Therefore, hand shift (countershaft speed changer) is the most general.
Along with the appearance of three speed and four gear transmissions, automaitc shfit (planetary pinion) speed changer has improved popularization along with the popular of automobile.These transmissions improved the operating characteristics and the fuel economy of vehicle.The quantity increase of velocity ratio has reduced the step-length between the velocity ratio, and therefore by the operator is discovered less than speed substantially than replacing the shift quality that improves speed changer.
Six speed transmission provides some advantages of relative four speed and five speed transmissions, comprises improved vehicle acceleration and improved fuel economy.Though many lorries adopt the power transmission with six or more forward velocity ratio, passenger vehicle still manufactures and has three speed and four gear transmissions, and because five fast or size and sophistications that six quick-mountings are put adopt their passenger vehicle less relatively.
Relative six speed transmission, seven speed, eight speed, nine speed and 10-speed transmission are providing further improvement aspect acceleration and the fuel economy.Yet, being similar to the six speed transmission of discussing above, the development of seven speed, eight speed, nine speed and 10-speed transmission is owing to complexity, size and cost are left out.
Summary of the invention
An object of the present invention is to provide a kind of improved speed changer, it has three in check planetary gear set, so that ten forward velocity ratios and a reverse speed ratio to be provided.
Speed changer series of the present invention has three planetary gear set, and it respectively comprises first parts, second parts and the 3rd parts, and these parts can comprise sun gear, ring gear or planet carrier component parts by any order.
Each carriage member can be single small gear carriage member (simply) or double pinion carriage member (compound).Embodiment with long small gear also is feasible.
First interconnecting member is connected the 3rd parts of first planetary gear set constantly with first parts of second planetary gear set.
Second interconnecting member is connected second parts of second planetary gear set constantly with the 3rd parts of the third line star gear train.
Input block is connected with second parts of first planetary gear set constantly.Output block constantly with second component interconnect of second planetary gear set.
First torque transmitter, break for example, it optionally is connected first parts of first planetary gear set with fixed component (gearbox case/housing).
Second torque transmitter, break for example, it optionally is connected the 3rd parts of second planetary gear set with fixed component (gearbox case/housing).
The 3rd torque transmitter, clutch for example, it optionally is connected second parts of first planetary gear set with first parts of the third line star gear train.
The 4th torque transmitter, clutch for example, it optionally is connected first parts of first planetary gear set with first parts of the third line star gear train.
The 5th torque transmitter, clutch for example, it optionally is connected the 3rd parts of first planetary gear set with second parts of the third line star gear train.
The 6th torque transmitter, clutch for example, it optionally is connected the 3rd parts of second planetary gear set with second parts of the third line star gear train.
These six torque transmitters can compare and a reverse speed ratio to produce ten forward velocity optionally with three combined engagement.
Various velocity ratios and velocity ratio scope (ratio spread) can realize by the gear ratio of selecting planetary gear set rightly.
From below in conjunction with accompanying drawing to the detailed description that realizes optimal mode of the present invention, will be easy to distinct above-mentioned feature of the present invention and further feature and advantage.
Description of drawings
Fig. 1 a is the schematic representation that comprises according to the dynamical system of planetary transmission of the present invention;
Fig. 1 b is the truth table and the chart of some operation characteristic of the dynamical system shown in the displayed map 1a; And
Fig. 1 c is the schematic representation of Fig. 1 a dynamical system of lever diagram form demonstration.
Embodiment
With reference to drawing, shown dynamical system 10 among Fig. 1 a, it has traditional motor and torque converter 12, planetary transmission 14 and traditional main reducing gear mechanism 16.Motor 12 can utilize various types of fuel to drive, to improve the efficient and the fuel economy of application-specific.This fuel can comprise for example gasoline, diesel oil, ethanol, dimethyl ether etc.
Planetary transmission 14 comprises input block 17, planetary gear system 18 that is connected with motor 12 constantly and the output block 19 that is connected with main reducing gear mechanism 16 constantly.Planetary gear system 18 comprises three planetary gear set 20,30 and 40.
Planetary gear set 20 comprises sun gear parts 22, ring gear component 24 and planet carrier component parts 26.Planet carrier component parts 26 comprises and a plurality ofly is rotatably installed on the carriage member 29 and is arranged to that both constitute the small gear 27 of meshing relation with sun gear parts 22 and ring gear component 24.
Planetary gear set 30 comprises sun gear parts 32, ring gear component 34 and planet carrier component parts 36.Planet carrier component parts 36 comprises and a plurality ofly is rotatably installed on the carriage member 39 and is arranged to that both constitute the small gear 37 of meshing relation with sun gear parts 32 and ring gear component 34.
Planetary gear set 40 comprises sun gear parts 42, ring gear component 44 and planet carrier component parts 46.Planet carrier component parts 46 comprises and a plurality ofly is installed on the carriage member 49 and is arranged to that both constitute the small gear 47 of meshing relation with ring gear component 44 and sun gear parts 42.
Planetary gear system also comprises six torque transmitters 80,82,84,85,86 and 87.These torque transmitters 80 and 82 are fixed torque transmitters, are commonly referred to break or reaction clutch.Torque transmitter 84,85,86 and 87 is rotary-type torque transmitters, is commonly referred to clutch.
Input block 17 is connected with the planet carrier component parts 26 of planetary gear set 20 constantly.Output block 19 is connected with the planet carrier component parts 36 of planetary gear set 30 constantly.
First interconnecting member 70 is connected the ring gear component 24 of planetary gear set 20 constantly with the sun gear parts 32 of planetary gear set 30.Second interconnecting member 72 is connected the planet carrier component parts 36 of planetary gear set 30 constantly with the ring gear component 44 of planetary gear set 40.
First torque transmitter, for example break 80, and it optionally is connected the sun gear parts 22 of planetary gear set 20 with gearbox case 60.Second torque transmitter, for example break 82, and it optionally is connected the ring gear component 34 of planetary gear set 30 with gearbox case 60.The 3rd torque transmitter, for example clutch 84, and it optionally is connected the planet carrier component parts 26 of planetary gear set 20 with the sun gear parts 42 of planetary gear set 40.The 4th torque transmitter, for example clutch 85, and it optionally is connected the sun gear parts 22 of planetary gear set 20 with the sun gear parts 42 of planetary gear set 40.The 5th torque transmitter, for example clutch 86, and it optionally is connected the ring gear component 24 of planetary gear set 20 and the sun gear parts 32 of planetary gear set 30 by interconnecting member 70 with the planet carrier component parts 46 of planetary gear set 40.The 6th torque transmitter, for example clutch 87, and it optionally is connected the ring gear component 34 of planetary gear set 30 with the planet carrier component parts 46 of planetary gear set 40.
As shown in Fig. 1 b, shown in the disclosed truth table in especially true place, these torque transmitters optionally engage with three combination, so that ten forward velocity ratios and a reverse speed ratio to be provided, all velocity ratios all have single transition gear shift (single transition shift) and four overdrive ratios.
As mentioned above, in the truth table of Fig. 1 b, shown the joint Schedule that is used for torque transmitter.The chart of Fig. 1 b has been described the ratio rank (ratio step) that reached in the above-mentioned speed changer.For example, the rank between first and second forward velocity ratio are 1.47 than (step ratio), and the rank between reverse speed ratio and first forward velocity ratio are than being-0.64.
Referring to Fig. 1 c, it has shown the embodiment of the dynamical system 10 shown in Fig. 1 a with the lever diagram form.Lever diagram is for example schematic representation of the member of automatic transmission of mechanical device.Each independent lever is represented a planetary gear set, and wherein three of planetary gear set basic mechanical components are respectively represented by a node.Therefore, single lever comprises three nodes: one is used for the sun gear parts, and one is used for the planetary gear carrier parts, and one is used for ring gear component.Relative length between the node of each lever can be used for representing the annular-fixed star lever ratio of each corresponding gear train.These lever ratios are used to change the gear ratio of speed changer again, to obtain suitable ratio and than progression (ratio progression).Mechanical coupling between the node of various planetary gear set or interconnect by thin horizontal line represents, and torque transmitter for example clutch and break are represented by staggered finger piece.If device is a break, so just with one group of finger piece ground connection (ground).At Benford, Howard and Leising, the SAE papers 810102 in 1981 of Maurice, can find the further specifying of form, purpose and purposes of lever diagram in " The Lever Analogy:A New Tool in TransmissionAnalysis ", this paper is combined in herein by reference and intactly.
Dynamical system 10 comprises the input block 17 that is connected with motor 12 constantly; The output block 19 that is connected with main reducing gear mechanism 16 constantly; The first planetary gear set 20A, it has three nodes: first node 22A, Section Point 26A and the 3rd node 24A; The second planetary gear set 30A, it has three nodes: first node 32A, Section Point 36A and the 3rd node 34A; And the third line star gear train 40A, it has three nodes: first node 42A, Section Point 46A and the 3rd node 44A.
Input block 17 is connected with node 26A constantly.Output block 19 is connected with node 36A constantly.
Node 24A is connected with node 32A constantly by interconnecting member 70.Node 36A is connected with node 44A constantly by interconnecting member 72.
First torque transmitter, for example break 80, and it optionally is connected node 22A with gearbox case 60.Second torque transmitter, for example break 82, and it optionally is connected node 34A with gearbox case 60.The 3rd torque transmitter, for example clutch 84, and it optionally is connected node 26A with node 42A.The 4th torque transmitter, for example clutch 85, and it optionally is connected node 22A with node 42A.The 5th torque transmitter, for example clutch 86, and it optionally is connected node 24A and node 32A by interconnecting member 70 with node 46A.The 6th torque transmitter, for example clutch 87, and it optionally is connected node 34A with node 46A.
In order to set up velocity ratio, three torque transmitters are engaged for each drive state.Engageable torque transmitting devices is by " X " representative in each the corresponding row among Fig. 1 b.For example, in order to set up the reverse gear ratio, break 82 and clutch 84 and 87 are engaged.Break 82 makes node 34A engage with gearbox case 60.Clutch 84 makes node 26A engage with node 42A.Clutch 87 makes node 34A engage with node 46A.Similarly, can obtain ten forward velocity ratios according to the joint combination of Fig. 1 b by different clutches.
Dynamical system 10 can be shared member with motor vehicle driven by mixed power, and this combination can be in " electric weight depletion-mode " operation down.For purpose of the present invention, " electric weight depletion-mode " is a kind of such pattern, mainly provides power by motor/generator for vehicle under this pattern, makes when vehicle arrives its destination, and storage battery is depleted or almost exhaust.In other words, during the electric weight depletion-mode, motor 12 just runs to guarantees storage battery not depleted necessary degree before arriving the destination.Traditional motor vehicle driven by mixed power is with " electric weight is kept pattern " operation, if when wherein the accumulator electric-quantity level drops to predetermined (for example, 25%) below horizontal, motor automatically operation with to charge in batteries.Therefore, by moving under the electric weight depletion-mode, motor vehicle driven by mixed power can keep some or all otherwise will be consumed to keep the fuel of the accumulator electric-quantity level in 25% the conventional hybrid power car.Should understand that if storage battery can recharge by being inserted in a certain energy dynamical system of motor vehicle driven by mixed power is preferred so only moves with the electric weight depletion-mode after arriving the destination.
Be used to realize optimal mode of the present invention though described in detail, the technician in field related to the present invention will recognize various alternative design of the present invention and the embodiments of putting into practice in the scope that belongs to appended claims.

Claims (3)

1. multiple-speed gear-box comprises:
Input block;
Output block;
First planetary gear set, second planetary gear set and the third line star gear train that respectively have sun gear parts, planet carrier component parts and ring gear component;
First interconnecting member, it is connected the described ring gear component of described first planetary gear set constantly with the described sun gear parts of described second planetary gear set;
Second interconnecting member, it is connected the described planet carrier component parts of described second planetary gear set constantly with the described ring gear component of described the third line star gear train;
First torque transmitter, it optionally is connected the described sun gear parts of described first planetary gear set with fixed component;
Second torque transmitter, it optionally is connected the described ring gear component of described second planetary gear set with fixed component;
The 3rd torque transmitter, it optionally is connected the described planet carrier component parts of described first planetary gear set with the described sun gear parts of described the third line star gear train;
The 4th torque transmitter, it optionally is connected the described sun gear parts of described first planetary gear set with the described sun gear parts of described the third line star gear train;
The 5th torque transmitter, it optionally is connected the described ring gear component of described first planetary gear set with the described planet carrier component parts of described the third line star gear train;
The 6th torque transmitter, it optionally is connected the described ring gear component of described second planetary gear set with the described planet carrier component parts of described the third line star gear train; And
Described six torque transmitters engage with three combination, to set up at least ten forward velocity ratios and at least one reverse speed ratio between described input block and described output block.
2. speed changer according to claim 1, it is characterized in that, described first torque transmitter and second torque transmitter comprise break, and described the 3rd torque transmitter, the 4th torque transmitter, the 5th torque transmitter and the 6th torque transmitter comprise clutch.
3. speed changer according to claim 1, it is characterized in that, described input block is connected with the described planet carrier component parts of described first planetary gear set constantly, and described output block is connected with the described planet carrier component parts of described second planetary gear set constantly.
CN2008101376914A 2007-07-09 2008-07-07 10-speed transmission Active CN101344155B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/774,877 US7828688B2 (en) 2007-07-09 2007-07-09 10-speed transmission
US11/774877 2007-07-09

Publications (2)

Publication Number Publication Date
CN101344155A CN101344155A (en) 2009-01-14
CN101344155B true CN101344155B (en) 2011-10-05

Family

ID=40157583

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2008101376914A Active CN101344155B (en) 2007-07-09 2008-07-07 10-speed transmission

Country Status (3)

Country Link
US (1) US7828688B2 (en)
CN (1) CN101344155B (en)
DE (1) DE102008032015B4 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7824298B2 (en) * 2007-03-30 2010-11-02 Gm Global Technology Operations, Inc. 8-speed transmission with two fixed interconnections
US8047951B2 (en) * 2008-01-25 2011-11-01 GM Global Technology Operations LLC Ten-speed transmission
US8128527B2 (en) * 2009-02-13 2012-03-06 GM Global Technology Operations LLC Multi-speed transmission
US8177675B2 (en) * 2009-02-13 2012-05-15 GM Global Technology Operations LLC Multi-speed transmission
WO2011006138A1 (en) 2009-07-09 2011-01-13 Cubic Corporation Transit account management with mobile device messaging
US8545361B2 (en) * 2009-08-05 2013-10-01 GM Global Technology Operations LLC Multi-speed transmission having three planetary gear sets
US8491437B2 (en) * 2009-08-05 2013-07-23 GM Global Technology Operations LLC Multi-speed transmission having three planetary gear sets
DE102012221239A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
DE102012221241A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
DE102012221235A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
DE102012221234A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
DE102012221238A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
DE102012221236A1 (en) 2012-11-21 2014-05-22 Zf Friedrichshafen Ag transmission
JP6264804B2 (en) 2013-09-25 2018-01-24 アイシン精機株式会社 Transmission
JP6233097B2 (en) 2014-02-28 2017-11-22 アイシン精機株式会社 Automatic transmission for vehicles
EP2921745A1 (en) 2014-02-28 2015-09-23 Aisin Seiki Kabushiki Kaisha Automatic transmission for vehicle
JP6265014B2 (en) 2014-04-04 2018-01-24 アイシン精機株式会社 Automatic transmission for vehicle
JP6394354B2 (en) 2014-12-16 2018-09-26 アイシン精機株式会社 Automatic transmission for vehicles
US10344831B2 (en) * 2015-06-04 2019-07-09 Hyundai Motor Company Transmission for vehicle
KR101724854B1 (en) * 2015-06-08 2017-04-10 현대자동차주식회사 Multy stage transmmission for vehicle
EP3150883A1 (en) * 2015-10-01 2017-04-05 ZF Friedrichshafen AG Transmission for a motor vehicle, and power train for a motor vehicle
DE102015223204A1 (en) 2015-11-24 2017-05-24 Holzma Plattenaufteiltechnik Gmbh Method for processing a plate-shaped workpiece, as well as panel dividing system for carrying out the method
KR101826559B1 (en) * 2016-03-08 2018-02-07 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6217474B1 (en) * 1999-10-22 2001-04-17 General Motors Corporation Multi speed power transmission

Family Cites Families (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4070927A (en) 1976-06-04 1978-01-31 General Motors Corporation Planetary gearing arrangement for a transmission
JPH06100251B2 (en) 1985-01-14 1994-12-12 株式会社小松製作所 Planetary gear type transmission
FR2656055B1 (en) 1989-12-18 1994-04-29 Lepelletier Pierre MULTI-SPEED AUTOMATIC TRANSMISSION FOR MOTOR VEHICLE.
US5385064A (en) 1992-10-23 1995-01-31 Borg-Warner Automotive, Inc. Dual clutch countershaft automatic transmission
US5497867A (en) 1993-12-27 1996-03-12 Eaton Corporation Synchronizer with cone cup locater pins
JP3161244B2 (en) 1994-08-26 2001-04-25 トヨタ自動車株式会社 Transmission synchronization device
US5560461A (en) 1995-02-24 1996-10-01 Dana Corporation Multiple cone synchronizer for vehicle transmission
US5651435A (en) 1995-07-31 1997-07-29 New Venture Gear, Inc. Reverse brake for manual transmissions
US5599251A (en) 1995-09-27 1997-02-04 Ford Motor Company Six speed automatic transmission for automotive vehicles
JP3710180B2 (en) 1995-10-31 2005-10-26 ジヤトコ株式会社 Gear transmission for automatic transmission
US5735767A (en) 1996-10-21 1998-04-07 New Venture Gear, Inc. Add-on two-speed compounder
US6071208A (en) 1998-06-22 2000-06-06 Koivunen; Erkki Compact multi-ratio automatic transmission
US6053839A (en) 1999-06-18 2000-04-25 Ford Global Technologies, Inc. Multiple speed overdrive transmission for a motor vehicle
US6083135A (en) 1999-06-18 2000-07-04 Ford Global Technologies, Inc. Multiple speed overdrive transmission for a motor vehicle
JP2001165250A (en) 1999-12-07 2001-06-19 Honda Motor Co Ltd Vehicular automatic transmission
JP2001173734A (en) 1999-12-15 2001-06-26 Honda Motor Co Ltd Vehicular automatic transmission
KR100354141B1 (en) 1999-12-15 2002-09-28 현대자동차주식회사 Synchronizer for Manual Transmission
US6422969B1 (en) 2000-08-14 2002-07-23 General Motors Corporation Powertrain with a six speed planetary transmission having three planetary gear sets
US6425841B1 (en) 2000-08-28 2002-07-30 General Motors Corporation Multi-speed power transmission
JP4438247B2 (en) 2001-03-29 2010-03-24 アイシン・エィ・ダブリュ株式会社 Automatic transmission for vehicles
US6634981B1 (en) * 2002-04-16 2003-10-21 General Motors Corporation Family of transmission mechanisms with three planetary gear sets and a stationary member
US6623397B1 (en) 2002-04-17 2003-09-23 General Motors Corporation Family of multi-speed transmission mechanisms with three non-continuously interconnected planetary gear sets
KR100444068B1 (en) 2002-06-27 2004-08-12 현대자동차주식회사 Hydraulic control system for an 6-shift automatic transmission in a vehicle
US6746360B2 (en) * 2002-09-12 2004-06-08 General Motors Corporation Transmission mechanisms with clutched input and a stationary planetary gear member
US7086986B2 (en) * 2004-06-04 2006-08-08 General Motors Corporation Wide ratio transmissions with two fixed interconnecting members and at least three clutches
US7118510B2 (en) * 2004-07-23 2006-10-10 General Motors Corporation Planetary transmissions having input clutches and two interconnecting members
US7150695B2 (en) * 2004-07-23 2006-12-19 General Motors Corporation Planetary transmissions having input clutches and three interconnected gear sets

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6217474B1 (en) * 1999-10-22 2001-04-17 General Motors Corporation Multi speed power transmission

Also Published As

Publication number Publication date
CN101344155A (en) 2009-01-14
DE102008032015B4 (en) 2017-08-17
DE102008032015A1 (en) 2009-01-29
US7828688B2 (en) 2010-11-09
US20090017967A1 (en) 2009-01-15

Similar Documents

Publication Publication Date Title
CN101344155B (en) 10-speed transmission
CN101344157B (en) 9-speed transmission
CN101344143B (en) 10-speed transmission
CN101319705B (en) 10-speed transmission
CN101344142B (en) 9-speed transmission
CN101344153B (en) 9-speed transmission
CN101290054B (en) Eight-speed transmission
CN101290050B (en) Eight-speed transmission
CN101290047B (en) Eight-speed transmission
CN101344145B (en) 8-speed transmission
CN101349332B (en) 8-speed transmission
CN101368620B (en) 8-speed transmission
CN101358641B (en) Eight-speed transmission
CN101344150B (en) 8-speed transmission
CN101344156A (en) 9-speed transmission
CN101319707B (en) 8-speed transmission
CN101319716B (en) 8-speed transmission
CN101275646A (en) 8-speed transmission with two fixed interconnection components
CN101319704B (en) 8-speed transmission
CN101344149B (en) 8-speed transmission
CN101349328B (en) 8-speed transmission
CN101290046B (en) Eight-speed transmission
CN101319714B (en) 8-speed transmission
CN101280830B (en) Eight speed automatic transmission
CN101373016B (en) 8-speed transmission

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant